JP2005511984A - Tensioner for timing belt with stopper controlled by friction brake - Google Patents

Tensioner for timing belt with stopper controlled by friction brake Download PDF

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Publication number
JP2005511984A
JP2005511984A JP2003549763A JP2003549763A JP2005511984A JP 2005511984 A JP2005511984 A JP 2005511984A JP 2003549763 A JP2003549763 A JP 2003549763A JP 2003549763 A JP2003549763 A JP 2003549763A JP 2005511984 A JP2005511984 A JP 2005511984A
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Japan
Prior art keywords
member
direction
pivot arm
tensioner
belt
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Granted
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JP2003549763A
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JP4508641B2 (en
Inventor
ジャセック ステップニアック
リチャード エイ フォレスト
マレック フランコウスキ
マッツ ケイ リポウスキ
ヨルマ ジェイ レートヴァーラ
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リテンズ オートモーティヴ
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Application filed by リテンズ オートモーティヴ filed Critical リテンズ オートモーティヴ
Priority to PCT/CA2002/001854 priority patent/WO2003048606A1/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H7/10Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1254Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
    • F16H7/1281Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path
    • F16H7/129Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path with means for impeding reverse motion
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00Freewheels or freewheel clutches
    • F16D41/20Freewheels or freewheel clutches with expandable or contractable clamping ring or band
    • F16D41/206Freewheels or freewheel clutches with expandable or contractable clamping ring or band having axially adjacent coils, e.g. helical wrap-springs
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H7/10Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1209Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means
    • F16H7/1218Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means of the dry friction type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H2007/0802Actuators for final output members
    • F16H2007/081Torsion springs
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H7/0829Means for varying tension of belts, ropes, or chains with vibration damping means
    • F16H2007/084Means for varying tension of belts, ropes, or chains with vibration damping means having vibration damping characteristics dependent on the moving direction of the tensioner
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H7/0829Means for varying tension of belts, ropes, or chains with vibration damping means
    • F16H7/0831Means for varying tension of belts, ropes, or chains with vibration damping means of the dry friction type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H7/0829Means for varying tension of belts, ropes, or chains with vibration damping means
    • F16H7/0834Means for varying tension of belts, ropes, or chains with vibration damping means of the viscous friction type, e.g. viscous fluid

Abstract

A tensioner (10) is provided with a reverse rotation stopper device (40) that allows a pivot arm (20) to freely rotate in one direction and not to rotate in the other direction. Under normal operating conditions, reversal is prevented by friction that can withstand the torque acting on the pivot arm (20) so that belt skipping does not occur. In the disclosed embodiment, the reverse stopper device (40) includes a stop sleeve (50) and a clamp holder (60) that are axially coupled and relatively rotatable. The clutch spring (80) surrounding them freely rotates the stop sleeve (50) and the clamp holder (60) relatively in one direction but not in the other direction. The clamp (70) held in the clamp holder (60) is in frictional engagement with the pivot shaft. Instead of a friction clamp, a viscous coupling device can be used.

Description

  The present invention generally relates to a belt tensioner for a vehicle, and more particularly to a timing belt tensioner in which the position of a reverse rotation stopper of an arm is controlled by a one-way clutch and a friction brake.

  Belt tensioners for vehicles are well known to those skilled in the art and are used to adjust the tension of various belt systems, such as timing belts. Generally, a belt tensioner includes a movable support structure that rotatably supports a portion of a belt in an engine or other mechanical device. The rotational position of the arm / pulley sub-assembly in the belt tensioner is usually self-adjusting and is due to the length of the belt path due to engine thermal expansion and contraction and / or due to belt wear and elongation. Adjust the belt tension by compensating for the increase and decrease of the belt length. Further, the entire tensioner assembly is typically manually adjustable relative to the engine block so that the tensioner can be adjusted to the proper position of the engine regardless of engine manufacturing tolerances.

  One common type of belt tensioner according to the prior art includes a fixed structure and a pivot structure, which is generally comprised of an arm / pulley sub-assembly and pivots to the fixed structure. Installed as possible. A coil spring surrounds the pivot member, and ends of the spring are coupled to the fixed structure and the pivot structure, respectively, and urge the pivot structure toward a position where the tension of the belt is maximized. As the pivot structure moves from a position where the belt tension is minimized to a position where the belt tension is maximized, the biasing force of the spring decreases. Although the spring force varies within a given range of motion, the belt is maintained in a substantially constant tension. U.S. Pat. No. 4,473,362 discloses such a tensioner.

US Pat. No. 4,473,362

  Further, the tensioner for the timing belt and the tensioner for the chain usually have a stroke limiter. Stroke limiters typically include a pair of fixed stoppers that prevent the pivot arm from rotating beyond a predetermined distance from its normal position. That is, the first stopper restricts the rotation of the arm toward the belt and is referred to as a “free arm stopper”, and the second stopper restricts the rotation of the arm away from the belt. ". The reversing stopper is arranged so that the belt does not float from any sprocket teeth in the drive system and does not "tooth jump" or disengage from the teeth even when the pivot arm is reversed. It is normal. In other words, the reversing stopper is designed to prevent tooth skipping, otherwise such tooth skipping will cause timing errors between the various sprockets, resulting in equipment malfunction and damage. It will be.

  A common way to position the reversing stopper at a predetermined distance from the nominal position of the pivot arm, such as when using a tensioner that does not provide initial manual installation adjustment and rotating the pivot structure to compensate for engine manufacturing tolerances. Is not convenient. In other words, in such a tensioner configuration, the tensioner arm does not have any fixed nominal position, and therefore there is no fixed position of the reverse stop, and therefore the initial tensioner's position. During the installation operation, it is necessary to adjust the position of the reverse rotation stopper manually or preferably automatically. In addition, the service life of engine parts has increased and the life of the belt and the belt have become longer, so that a wider range of adjustment is required for the tensioner pivot structure during the life of the tensioner. . Accordingly, it is more important to automatically adjust the position of the reverse rotation stopper in order to avoid manual maintenance adjustment.

  Several known tensioner designs provide such automatic adjustment of the reverse stop in the tensioner. For example, in US Pat. No. 4,145,934, once the tensioner arm is urged against the belt by a tension spring by pressing the wedge against the eccentric arm (lever), The arm is prevented from rotating away from the belt. Similarly, the tensioner disclosed in US Pat. No. 4,351,636 is identical in principle, but uses a ratchet pawl assembly instead of a wedge. U.S. Pat. No. 4,634,407 discloses another ratchet pawl tensioner mechanism. However, in these patents, once the tensioner arm is rotated toward the belt, it is impossible for the arm to rotate away from the belt, so in such a configuration, The belt tension cannot be controlled while the engine block is thermally expanded.

U.S. Pat. No. 4,145,934 US Pat. No. 4,351,636 US Pat. No. 4,634,407

  U.S. Pat. No. 4,583,962 discloses an improvement to such a design. More specifically, the mechanism disclosed in that patent is adapted to the thermal expansion of the engine by allowing a limited amount of return stroke such that the arm goes to the reverse stop. The tensioner according to the patent uses a one-way device of a spring clutch type and an arcuate slot configured to allow the arm to reverse. Similarly, the tensioners disclosed in U.S. Pat. No. 4,822,322 and U.S. Pat. No. 4,834,694 are all connected by a conventional (roller) one-way clutch. A direction mechanism is constructed and the return stroke of the tensioner arm is controlled by an arcuate slot. Further, in the tensioner disclosed in U.S. Pat. No. 4,808,148, the retrograde stroke is not limited by a slot, but elastically attached between the ratchet pawl assembly and the stationary mounting member. A biasing element (eg, an elastomeric spring) is provided.

US Pat. No. 4,583,962 US Pat. No. 4,822,322 US Pat. No. 4,834,694 U.S. Pat. No. 4,808,148

  The tensioner of any of the above-mentioned designs has the restriction that once the reversing stopper is moved away from the belt, once the arm is moved toward the free position of the arm, and when the engine is operated under conditions other than the optimum driving conditions. Had. The reversing stopper moves beyond the optimum position during cold start and / or due to severe kickback of the engine, so the tensioner arm often comes into contact with the reversing stopper, which causes noise and damage And / or cause premature failure of the part. Further, in such a type of tensioner, the belt cannot be reinstalled or replaced.

  The tensioner disclosed in U.S. Pat. No. 4,923,435 places a viscous material between the arm and the one-way clutch mechanism. However, this design does not guarantee that the tensioned belt will not fly out. When a continuous load is applied to the belt (this condition occurs especially when the engine is forced to reverse by reversing the vehicle while the engine is stopped), the viscous material allows the tensioner arm to rotate. Therefore, the viscous material does not function as an active stopper, but functions as a mere rotating damper.

U.S. Pat. No. 4,923,435

  The present invention overcomes these limitations of the prior art, and in the provided tensioner, the reverse stopper "follows" as the tensioner arm pivots toward the free position of the arm. This can automatically “find” the proper operating position of the reverse stop, while the reverse stop operating position is maintained under nominal or temporary (eg vibration) belt loads. For example, at the time of installation, the reverse rotation stopper can be manually rotated, and the reverse rotation is allowed when a high load continues sufficiently or for a long time on the belt.

  A timing belt tensioner according to an aspect of the present invention includes a pivot shaft fixed to an engine block, a pivot arm pivotally attached to the pivot shaft, and a pivot arm and a fixing structure (for example, an engine block). And a torsion spring which is attached therebetween and urges the pivot arm in a direction in which the belt is stretched (that is, toward the free position of the arm), and a reverse stopper device. The reverse stopper device includes a substantially cylindrical stop sleeve, a friction brake (eg, supported by a substantially cylindrical clamp holder), and a one-way clutch. The stop sleeve and the pivot arm are preferably configured in cooperation so that the pivot arm can rotate by a predetermined limited amount relative to the stop sleeve. The one-way clutch allows a relatively free rotational movement in the direction in which the stop sleeve (and hence the pivot arm) moves to the free position of the arm, but in the direction in which the stop sleeve moves away from the belt (ie, the belt tension is minimal). When rotating (toward the position), the stop sleeve engages the friction brake, which effectively “fixes” the one-way clutch at a fixed location, such as the pivot shaft or the engine block itself. “Yes. As a modification, instead of the friction brake, for example, a hydraulic coupling device such as one using a viscous substance may be used.

  When the crankshaft is reversed, the friction brake can prevent the arm from moving toward a position where the tension of the belt is minimized depending on the force applied from the belt. When the pivot arm is rotated manually during installation or the like, the reverse rotation stopper allows or “releases” the rotation of the reverse rotation stopper toward a position where the belt tension is minimized. According to the tensioner according to the configuration of the present invention, the installation becomes easy and the configuration is simple, so that the time and cost of manufacturing and installation can be reduced.

According to another aspect of the present invention, a rotating device for selectively transmitting rotational output or rotational torque is directly coupled to each other in the axial direction and can be rotated relative to each other. The rotation member is included. When the one-way clutch spring is disposed so as to be placed on the pair of rotating members and one of the rotating members rotates in one direction, the pair of rotating members are interlocked in the rotating direction (that is, between the two) Relative rotation is prevented) and when one of the rotating members rotates in the opposite direction, the rotating member is allowed to rotate relatively. One of the rotating members may have an edge that restrains the winding of the clutch spring from opening, and the clutch spring has a diameter that is larger than the remaining winding. It may have one or more windings and provide some free stroke before the clutch spring interlocks the rotating member in the direction of rotation.
Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

  FIG. 1 shows a timing belt device for an internal combustion engine. A toothed pulley and sprocket 112 is fixed to the crankshaft 113 of the engine, and a belt 114 having teeth on the inner surface is driven by the sprocket 112. The toothed belt 114 pulls and drives a second sprocket 116 with teeth on the outer surface, which is connected to the camshaft 118 of the engine and thus rotates the camshaft. The tensioner 10 according to the present invention is attached in such a relationship as to apply tension to the belt 114.

  As shown in FIG. 2, the pulley 12 included in the tensioner 10 is attached to a ball bearing assembly 13 and extends to the outer periphery of the pivot arm 20, and the pivot arm 20 is, for example, a journal bearing. It is attached to the pivot shaft so that it can be eccentrically pivoted with respect to the pivot shaft 16. In other words, the pulley 12 rotates about the rotation axis 15 of the pulley itself, passing through the center of the ball bearing assembly 13, and the pivot arm 20 is centered on the longitudinal axis 16c of the pivot shaft 16 (the pulley 12 While pivoting together, the axis 16c is generally spaced and parallel to the rotational axis 15 of the pulley 12.

  The pivot shaft 16 has a bore 16b penetrating in the center in the longitudinal direction, and the tensioner assembly is fixed to the engine by installation bolts (not shown) passed through the bore. A base plate 30 is attached to the pivot shaft 16 by press fitting. In a preferred configuration, the base plate has a protrusion 31 at the center in order to improve the press fitting between the base plate and the pivot shaft.

  A torsion coil spring 18 surrounds the lower portion (in the figure) of the tensioner and is mounted between the arm 20 and the base plate 30 so that one end projection 18a of the spring extends into a corresponding slot 22 in the arm 20. The protrusion 18 b at the other end of the spring extends into a slot 33 formed in the outer skirt 32 extending upward of the base plate 30. When the tensioner 10 is assembled, before the arm 20 is brought to the final axial position, the arm 20 is rotated with respect to the base plate 30 to apply a preload to the spring 18 so that the arm 20 is brought into the free position of the arm. Energize to rotate toward. A thrust washer 14 is disposed between the main body of the arm 20 and the flange 16a of the pivot shaft 16 to reduce friction between the two when the arm 20 rotates.

  A reverse stopper device 40 is installed between the arm 20 and the base plate 30 in the pivot shaft 16. In one embodiment, the reverse stopper device 40 comprises a generally cylindrical stop sleeve 50, a generally cylindrical clamp holder 60 that is directly coupled together, a friction brake member in the form of a clamp 70, The clutch spring 80 and the bushing 100 are configured. The friction clamp 70 shown in detail in FIG. 4 is held in the clamp holder 60 and is in frictional rotational engagement with the pivot shaft 16 so that the clamp holder 60 and the friction clamp 70 are together or in a single unit. This unit is configured to rotate with respect to the pivot shaft 16.

  In one preferred embodiment, the stop sleeve 50 extends along a circumference with a flange-like outward projection 56 to directly couple the clamp holder 60 to the stop sleeve 50. An outward groove portion 54 is provided, and the projection portion and the groove portion are fitted into an inward groove 68 and an inward ring 67 provided in the clamp holder 60, respectively. As shown in FIG. 3, the end portion of the stop sleeve 50 where the protrusion 56 and the groove 54 are arranged is divided into a plurality of narrow and flexible finger portions 59 by an axial cut 53. Yes. Since the finger-like portion 59 is flexible in the radial direction, if the projection 56 is narrowed down to be inserted into the inward ring 67 of the clamp holder 60 and the two parts are assembled with each other, then the projection Rebounds back to its original position. The protrusions, the ring, and the grooves are engaged with each other, so that the stop sleeve 50 and the clamp holder 60 are mutually locked in the axial direction while being relatively rotated. The stop sleeve 50 and the clamp holder 60 are fitted with a gap between each other, and these two parts can rotate relatively freely. The stop sleeve is made of a flexible material such as nylon and can be bent inward or rebounded outward.

  A bushing 100 is inserted inside the stop sleeve 50 to prevent the protrusion 56 from collapsing inward during the operation life of the tensioner. The bushing 100 also improves the overall rigidity of the stop sleeve 50, particularly when the stop sleeve 50 prevents the arm from rotating.

  The clamp 70 is designed to grip the pivot shaft 16 via a pad or brake shoe-like element 71 to substantially or “selectively” secure the clamp 70 with a predetermined force. Thus, the clamp holder 60 is fixed to the pivot shaft 16. The clamp 70 is designed to grip the pivot shaft 16 with sufficient force, and frictionally slides the clamp 70 against the pivot shaft 16 by overcoming the frictional resistance force between the pad element 71 and the pivot shaft 16. (1) Although the magnitude of the torque required for rotating the clamp holder 60 is larger than the magnitude of the torque generated by the force acting from the belt under the condition that no tooth jump occurs (1) (2) When a torque load exceeding the design gripping torque of the clamp 70 is applied, the clamp 70 (and hence the clamp holder 60) can be rotated. Desirably, the clamp 70 is made from a corrosion resistant material with high yield strength, such as 17-4 stainless steel, and the required preload force can be reached by greatly deforming its spring element. It is a thing. As a variant, it is also possible to produce a clamp from high-strength carbon steel or tool steel and apply a corrosion-resistant coating to the part.

  In one preferred form, as shown in FIG. 4, the clamp 70 resembles the letter “C” with pads or brake shoe-like elements 71 attached to both ends. When the clamp 70 is manufactured in such a shape, it is preferable that the clamp 70 is provided with a tab 72 to assist the positioning of the clamp and the engagement and fixing to the clamp holder 60. The friction clamp 70 extends in a part of the circumference of the clamp holder 60, and a part of the friction clamp 70 is fitted in a groove 73 that penetrates in the radial direction. The pads 71 are passed through openings 74 (one provided on each side of the clamp holder) that completely penetrate the wall surface of the clamp holder 60 from the bottom of the groove 73 to grip the side surface of the pivot shaft 16. Be able to. In addition, tabs are formed between the two ribs 75 (only one of which is visible in FIG. 3) and are formed in the groove 73 and formed in the groove 73 (hidden and not visible in the drawing). 72 is inserted. Thereby, the tab 72 helps to position and maintain the friction clamp 70 in the clamp holder.

  The stop sleeve 50 and the clamp holder 60 have cylindrical outer surfaces 52 and 62, respectively, so as to span at least a portion where the stop sleeve 50 and the clamp holder 60 are coupled to each other. It has the same diameter. The clutch spring 80 is pressure-bonded so as to cover the cylindrical surfaces 52 and 62. One end of the clutch spring 80 is an axial protrusion 82, which is formed in the tongue piece 50 a extending in the axial direction from the stop sleeve 50 and extending in the axial direction 51. The protrusion 82 rotates the clutch spring 80 together with the stop sleeve 50. The clutch spring 80 and the two cylindrical surfaces 52 and 62 perform a one-way clutch function. That is, the pulley 12 and the pivot arm 20 rotate toward the belt 114, whereby the stop sleeve 50 is clamped to the clamp holder 60. The clutch spring 80 is slidably rotated with respect to the clamp holder 60 with little resistance when rotating in one direction with respect to the belt 114, but the pulley 12 and the pivot arm 20 are separated from the belt 114. When the rotation of the stop sleeve rotates in the opposite direction, the clutch spring 80 tightens and locks all three parts (stop sleeve 50, clamp holder 60, clutch spring 80). More specifically, when the winding direction of the clutch spring 80 is selected, the stop sleeve 50 (this is the pivot arm 20 as will be described in detail later) in the direction in which the belt is stretched (that is, the direction toward the free position of the arm). Can rotate freely with respect to the clamp holder 60, but when the stop sleeve 50 is rotated by the arm 20 in a direction in which the belt tension is minimized, the clutch spring 80 is in contact with the cylindrical surfaces 52 and 62. Are firmly clamped and tightened to prevent the stop sleeve 50 from rotating relative to the clamp holder 60 in a direction that minimizes the tension of the belt.

  The force acting between the pivot arm 20 and the stop sleeve 50 tends to press the clamp holder 60 axially against the base plate 30 together with the force acting between the stop sleeve 50 and the clamp holder 60. Therefore, it is desirable to form the bottom surface of the clamp holder 60 so as to provide a good thrust bearing surface.

  The spring clutch can be variously configured and arranged according to the arrangement of the coil spring 80. It will be understood that the torque transmission capability of the clutch spring depends on the number of turns of the coil engaged with each surface. If there is sufficient axial space for several coils, the clutch spring 80 may be evenly or substantially uniformly placed over the respective portions of the stop sleeve 50 and the clamp holder 60. However, if the space in the axial direction is limited, one of the cylindrical surfaces may be shortened and the clutch spring may be engaged with the element using a protrusion as illustrated in FIG. However, even in such a case, in order to reduce the magnitude of the force received by the protrusion, it is preferable to cover at least two to three coils on each cylindrical surface. Further, in order to improve the degree of sliding rotation of the clutch spring toward the free position of the arm, a stop sleeve having a ring-shaped edge 50c is provided so as to sufficiently cover at least one stroke of the clutch spring 80. Preferably it is provided. The ring-shaped edge 50c prevents the coil of the clutch spring from opening excessively before the clutch spring begins to slide relative to the clamp holder 60.

  The pivot arm 20 has a cavity 21 formed therein, and a tongue piece 50a of the stop sleeve 50 is fitted therein. Although the cavity 21 may be an interference fit with the tongue piece 50a, the pivot arm 20 is slightly more than the stop sleeve 50 by making the cavity slightly larger than the tongue piece 50a in the axial direction. It is preferable to be able to rotate freely. In order to minimize wear of the reverse stop device 40, the magnitude of such rotational “play” is at least approximately the magnitude of the rotational movement of the arm due to engine thermal expansion and / or the magnitude of vibration of the arm by the dynamic engine. It is recommended that they be identical. Such an angular range varies with the individual engine structure, but is generally on the order of 20 ° to 50 °. The pivot arm 20 is formed with a hexagonal hole 23. The hexagonal hole 23 has a corresponding tool such as an Allen wrench (registered trademark of a hexagonal bar wrench: not shown) or any other convenient lever type. Or a handle-type device can be accessed, and such a tool is inserted through the opening 14a of the thrust washer 14 into the hexagonal hole 23.

  5 and 6 show a tensioner according to another configuration of the present invention. This configuration is similar to that shown in FIG. 2, but the configuration of the reverse stop device 140 is somewhat modified and the pivot arm can be locked in the rotational direction relative to the stationary element of the tensioner. There is provided a mounting clip (not shown) constructed from any mechanical device. More specifically, in the reverse rotation stopper device 140, the configurations of the stop sleeve 150 and the clamp holder 160 are reversed as compared with the above-described embodiment, and an axial spring at the end of the clutch spring 180. The protrusion 182 is fixed in the hole 161 formed in the clamp holder 160 (not the stop sleeve 50 shown in FIG. 2). As a result, the cylindrical outer surface 152 of the stop sleeve 150 is preferably longer than the corresponding cylindrical outer surface 162 of the clamp holder 160 to accommodate the appropriate number of turns of the spring coil. The inward ring 157 and the inward groove 158 are formed in the stop sleeve 150 so that the portion 166 and the outward groove 164 are formed in the clamp holder 160 and are engaged with each other. Is required. Accordingly, an axial cut 163 forming a flexible finger 169 that facilitates assembly of the parts is formed in the clamp holder 160 as shown in FIG. Similarly, an edge 160 c that restricts excessive opening of the clutch spring 180 is formed in the clamp holder 160. Compared to the stop sleeve 150, the clamp holder 160 rarely receives any side force, and the clamp holder 160 needs to rotate relative to the pivot shaft 16 only under high torque conditions. Thus, no bushing can be provided between the clamp holder 160 and the pivot shaft 16.

  Further, the clamp holder 160 and the friction clamp 170 in the present embodiment are configured such that the friction clamp 170 fits into the groove 173, and the groove is formed as a groove hole that completely penetrates the diameter of the clamp holder 160. The pad 171 is exposed and engaged with the side surface of the pivot shaft 16. The tab 172 projects outward from the friction clamp 170 (projected inward in the embodiment of FIG. 4) and fits into a radial slot 176 extending perpendicular to the groove 173. Thus, the friction clamp 170 is properly positioned and held in the groove 173. The friction clamp 170 is pushed laterally into the groove or slot 173 and inserted into the clamp holder 160. Once the tab 172 is aligned with the slot 176, the friction clamp is moved radially to cause the tab 172 to move radially. Is engaged with the slot 176.

  The mounting clip facilitates the task of attaching the tensioner to the engine. More specifically, with the pivot arm 20 close to the rearmost position of the reverse rotation stopper or fully rotated, the pivot arm 20 and any stationary part or element in the tensioner 10 (eg, the base plate 30). A clip is inserted into a correspondingly provided hole, which is usually performed in an assembly line during the manufacture of the tensioner. With the installation clip inserted, the pivot arm 20 cannot rotate away from the initial factory setting until the installation clip is removed.

  7 and 8 show a tensioner according to still another configuration of the present invention. Although the overall configuration is similar to that of FIGS. 5 and 6, the configurations of the friction clamp 270 and the clamp holder 260 are different. More specifically, unlike the friction clamps 70 and 170 in the previous embodiment, the friction clamp 270 is configured in a split ring shape, and the friction clamp 270 has a wider circumference compared to the two previous embodiments. In range, it is configured to make frictional contact with the pivot shaft of the tensioner. For example, the friction clamp 270 preferably contacts over 270 ° around the circumference of the pivot shaft.

  The friction clamp 270 is preferably made from a stainless steel spring wire. For reference, the friction clamp 270 in the illustrated embodiment is a 3 mm × 3 mm square, although the size of the spring wire of the friction spring clamp 270 will, of course, depend on the amount of torque that the friction clamp is required to hold. It is made from a spring wire with a cross section. It has been found that the friction clamp 270 is generally easier to make and stronger than the friction clamps 70 and 170 described above and provides a more consistent torque resistance performance.

  Furthermore, the sliding rotation performed by the clamp 270 is slightly different from the clamps of FIGS. When the protrusion 271a is pushed by the upper clamping sleeve 260a, the clamp 270 opens slightly, reducing the clamping force and frictional resistance to rotation. In other words, the friction brake is configured to open at least partially under conditions where release of friction retention is expected. As a result, the influence of the fluctuation of the friction coefficient on the torque at which the friction brake is released / slided is reduced.

  To accommodate the friction clamp 270, the clamp holder 260 is formed of two parts: an upper clamp sleeve 260a and a lower bottom sleeve 260b. As best shown in FIG. 8, the friction clamp 270 fits within a “pocket” defined by a shoulder surface 283 and a peripheral wall 284 in the clamp sleeve 260a.

  Three struts or tenons 285a, 285b, 285c protrude from the peripheral wall 284, and the related portions of the peripheral wall 284 are "thickened" accordingly. A portion of the peripheral wall 284 where the tenon 285c is formed has a hole penetrating the portion (not visible in the drawing), and the hole is formed in the peripheral wall 284 (in the direction of FIG. 7). In the lower surface (when the clamp sleeve 260a is disposed on the upper surface), a transition is made to a slot 286 formed in the radially outer surface 287 of the tenon 285c. The hole and the slot 286 are configured to receive the full length or almost the full length of the lower protrusion 282 extending in the axial direction of the clutch spring 280, and appropriately hold the lower protrusion 282. Secures the clutch spring 280 to the clamp sleeve 260a (and to the clamp holder 260 after assembly) in the rotational direction.

  Two notches or grooves 288a and 288b are formed on the peripheral wall 284 of the clamp sleeve 260a, one on each side of a tenon 285c configured to receive the axial projection 282 of the clutch spring 280. As well shown in FIG. 8, notches or grooves 288a, 288b receive the protruding ends of the friction clamp 270. One notch 288a is relatively narrow and accepts a corresponding end 271a of the friction clamp 270 with an interference fit to hold the end 271a of the friction clamp 270 firmly in place while the other The notch 288b is relatively wide and fits to assembly errors.

  The portion of the clamp sleeve 260a that engages with the clutch spring 280 preferably has a relatively large coefficient of friction in order to facilitate gripping of the clamp sleeve 260a by the clutch spring 280. On the other hand, the portion of the clamp sleeve 260a that rotatably engages the stop sleeve 250 preferably has a relatively small coefficient of friction to facilitate relative rotation of the two parts. Furthermore, the flexible finger 269 of the clamp sleeve 260a should have sufficient elasticity so that it will not break when the stop sleeve 250 and the clamp sleeve 260a are pressed together. In view of these various considerations, to achieve such a goal, the clamp sleeve 260a can be made by integrally molding different materials, each having the desired coefficient of friction and flexibility, or 3 A clamp sleeve is made from a material (eg nylon-46) chosen to satisfy all three items simultaneously.

  The bottom sleeve 260b generally has three main roles. The first is to surround the friction clamp 270 at a suitable location inside the clamp holder 260. Second, by “tying” the three tenons 285a, 285b, 285c to each other, the unit combining the friction clamp 270 and the clamp sleeve 260a can be combined with the axial projection 282 of the clutch spring 280 and the cylinder of the clamp sleeve 260a. The torsional load acting on the clamp sleeve 260a by the clutch spring 280 wound around the outer surface is to withstand better than when only one tenon 285c receives the torsional load. Third, the bottom surface 289 (when arranged in the orientation of FIG. 7) of the bottom sleeve 260b functions as a thrust bearing so that the reverse stopper device 240 is subjected to the base plate 230 under the axial load generated in the tensioner. When pressed against the base plate 230, the base plate 230 is allowed to rotate. Since the reverse stopper 289 functions as a thrust bearing surface, the bottom sleeve 260b is preferably formed from a material such as unfilled nylon having a relatively small coefficient of friction μ.

  As further shown in FIGS. 7 and 8, the bottom sleeve 260b has a substantially cylindrical peripheral wall 290 and a ring-shaped end “wall surface” 291. The exposed portion of the wall surface is A bottom surface 289 is provided that functions as a thrust bearing surface. The peripheral wall 290 protrudes radially outward over some portion 292 to provide a space into which the projecting clamp ends 271a and 271b can be fitted when the clamp holder 260 is assembled. Further, a slot 293 passes through in the axial direction of the ring-shaped end wall 291, and when the clamp holder 260 is assembled (with the remaining components of the tensioner), the tenon 285 c (in the axial direction of the clutch spring 280). The protrusion 282 extends into the groove 293 (with the protrusion 282 disposed in the groove 286 of the tenon 285c) (but does not protrude beyond the bearing surface 289). Two further slots are formed as blind holes in the upper surface of the end wall 291 that is ring-shaped, and these blind holes are the other two tenons 285a and 285b when the clamp holder 260 is assembled together. Arranged to accept.

  The peripheral wall 290 of the bottom sleeve 260b has a bead 294 that projects around the circumference of the inner surface of the peripheral wall 290, which is located near the upper edge (in the illustrated arrangement) of the peripheral wall 290. ing. The bead 294 engages with a circumferentially extending narrow locking groove 295 formed around the peripheral wall 284 of the clamp sleeve 260a. Thus, once the friction clamp 270 is properly positioned in the “pocket” of the clamp sleeve 260a, the clamp sleeve 260a and the bottom sleeve 260b are pushed together to snap the bead 294 into the locking groove 295. Assembling the clamp holder 260, the tenons 285a, 285b and 285c are inserted into the respective slots formed in the end wall 291 which is the ring shape of the bottom sleeve 260b.

  The bottom sleeve 260b has a ring-shaped upper edge (not visible in the drawing) around the upper edge (in the arrangement of FIG. 7) of the peripheral wall 290, the structure of which is shown in FIG. The edge 50c is the same as the edge 160c shown in FIG. The size of the ring-shaped edge accommodates one or more coils below the clutch spring 280 when the tensioner is assembled and before the spring begins to slide relative to the clamp holder 260, the clutch spring 280 It is determined to prevent the coil from opening excessively.

  The tensioner (especially the reverse stopper devices 40, 140, 240) operates as follows. When initially installing the tensioner and belt, the tensioner is typically placed in the proper position on the engine using bolts (not shown) that are inserted through the bore 16b of the pivot shaft 16 and the engine screw holes. It is attached. If the tensioner has the mounting clip 11, the arm 20 is already in a state where the tension of the belt is minimized, and the belt can be easily attached. Otherwise, if the tensioner does not have a mounting clip (especially when the tensioner is reinstalled during field maintenance and the clip is no longer available), the operator installing the tensioner must In order to hang the belt on the pulley 12, the pivot arm 20 must be moved to or near the position where the belt tension is minimized. For this purpose, an Allen wrench is inserted into the hexagonal hole 23 of the pivot arm 20 to rotate the pivot arm 20 to a position where the belt tension is minimized. There is a rotational clearance between the axial tongues 50a, 150a, 250a and the cavity 21 formed in the pivot arm 20, and some rotational “play” between the pivot arm 20 and the stop sleeves 50, 150, 250. If there is, the only rotational resistance force that the operator first feels is the force provided by the main spring 18. Once the “play” is exceeded, the operator must further rotate the stop sleeves 50, 150, 250. Since the stop sleeves 50, 150, 250 are fixed to the pivot shaft 16 in a rotational direction with a certain degree of strength via the friction clamps 70, 170, 270, the operator can connect the clamps 70, 170, 270 and the pivot shaft It is necessary to overcome the rotational resistance caused by friction between the two. The frictional resistance is designed to be large enough to withstand the torque caused by the belt force resulting from the reverse rotation of the engine, but small enough for the operator to reverse the pivot arm 20. Therefore, the operator can completely move the pivot arm 20 to a position where the tension of the belt is minimized, and the belt is attached to various sprockets and pulleys at this position.

  After placing the belt on various pulleys, the pivot arm 20 (and pulley 12) needs to be able to pivot freely towards the belt to provide the appropriate belt tension. If the tensioner has a mounting clip 11, the operator simply removes the clip 11. If the arm and pulley assembly is rotated manually to a position where the belt tension is minimized, the operator can release the force applied to the tool (Allen wrench) Main spring 18 rotates pivot arm 20 (and pulley 12) toward the belt. Once the pulley 12 is securely attached to the belt, the tool is removed and the manual installation process is terminated. In either case, the main spring 18 provides the movement of the arm towards the belt and consequently the belt can be tensioned, since the reverse stop device rotates the pivot arm 20 towards the free position of the arm. This is because no resistance is caused.

  Normally, the tensioner is sometimes subjected to certain engine operating conditions in which the belt load on the pulley increases and torque is applied to the pivot arm 20 in the reverse direction, i.e. away from the belt. Two such operating conditions are normal thermal expansion following a cold start of the engine and engine reversal. In any of these examples, if there is any rotation “play”, the tongues extending in the axial direction of the stop sleeves 50, 150, 250 after the pivot arm 20 is reversed toward the reverse stopper. 50a, 150a, 250a abuts the associated end face of the cavity 21 of the pivot arm 20, or the pivot arm is stopped if the axially extending tongue and cavity are an interference fit. There is no rotation with respect to the sleeve. Thereafter, the reverse rotation of the pivot arm 20 (ie, rotation away from the belt) is prevented, since the pivot arm is connected to the friction clamp via a stop sleeve, a spring clutch and a clamp holder. The friction clamp provides sufficient friction force to prevent such reversal and prevents tooth skipping, but the friction brake can be forcibly rotated by hand to easily install the tensioner arm Or can be re-installed.

  In the embodiment described above, the spring clutch provides the necessary one-way function. However, any known one-way device can be used to interconnect the stop sleeve to the friction brake (eg, one-way roller clutch, ratchet pawl, etc.). Similarly, instead of a clamp, the friction brake can be any known structure that produces a braking force by friction.

  As a modified example, as shown in FIG. 9, instead of the friction brake, a sufficient resistance force is generated to have a sufficient holding force to prevent the reverse rotation of the reverse rotation stopper and the arm from being separated from the belt. The tensioner can also be configured using a hydraulic device designed in this way. Such a hydraulic device may be any existing hydraulic device or, for example, pending US patent application Ser. No. 09 / 547,108, filed April 11, 2000, the disclosure of which is here And may be used as a viscous coupling assembly as disclosed in U.S. Pat.), Which still benefit from the various features of the present invention. In such a coupling assembly 340, the viscous material 370 has a first member 381 fixed to the lower outer surface of the pivot shaft 16 and a second member that can rotate with respect to the first member 381. (Second member 396 is shown as a unitary structure for illustrative purposes, but is shown in said US patent application Ser. No. 09 / 547,108). Thus, it is possible to make a two-part structure of the upper side and the lower side.) When a torsional load is suddenly applied to the pivot arm 320 and the load is transmitted to the second member 396 via the stop sleeve 350 and the clutch spring 380, the viscous material 370 is applied to the first member 381 due to its viscosity. In contrast, the second member 396 is prevented from rotating, but when the torsional load is applied gradually and / or continuously, the viscous material 370 causes the second member 396 to rotate relative to the first member 381. Allow to do.

Stop sleeve 350 is coupled to second member 396 by similar means as described above, although somewhat shorter than that described above. More specifically, the mutual coupling of the two parts locks them together in the axial direction but allows one part to rotate relative to the other part. The clutch spring 380 clutches the stop sleeve 350 against the second member 396 in substantially the same manner as the stop sleeve was clutched to the clamp holder in each of the embodiments described above. By providing rotational “play” with the stop sleeve 350 (for example, the cavity 321 in which the axial tongue 350a of the stop sleeve 350 is fitted is compared to the axial tongue 350a). The magnitude of vibration that the hydraulic device is subjected to can be reduced. Thereby, the service life of the hydraulic device can be extended.

  10 and 11 show a tensioner according to still another embodiment of the present invention. In this embodiment, the “stop sleeve” 450 is formed as an integral extension of the tensioner pivot arm 420. In this embodiment, the clutch spring 480 is directly and effectively coupled to the tensioner pivot arm 420, and the axial protrusion 482 of the clutch spring 480 is formed in the cavity 421 formed on the tensioner pivot arm 420. Extending inward (alternatively, the lower end opposite the clutch spring 480 may be secured to the “clamp sleeve” 460 in any suitable manner).

  As best shown in FIG. 11, the friction brake 470 is formed in a cylindrical shape that surrounds the lower portion of the pivot shaft 16 and lacks a cylindrical portion 472. A “clamp sleeve” 460 is coaxial with the friction brake 470 and is fitted to the outer surface of the friction brake. The clamp sleeve 460 has a key 462 that protrudes radially inward from the inner surface of the clamp sleeve 460, and the key 462 is fitted in the missing portion 472 of the friction brake 470. Accordingly, when the clamp sleeve 460 is sufficiently rotated to contact the wall surfaces 473 and 474 of the missing portion 472 and a sufficient force is applied, the friction brake 470 is rotated about the pivot shaft.

  It will be appreciated that the clamping sleeve 460 rotates relative to the tensioner pivot shaft 16 and that the pivot arm 420 is caused by transmitting torque via the clutch spring 480. If the “stop sleeve (which is essentially an extension of the center of the tensioner arm 420)” 450 has a sufficiently large number of turns of the coil and / or the shaft of the clutch spring The clutch spring 480 follows the movement of the pivot arm 420 of the tensioner if the directional protrusion 482 is firmly secured in the cavity 421 as shown.

  However, the tensioner has a slight “free stroke” so that the tensioner arm 420 is free to some extent (such as to accommodate engine thermal expansion and / or dynamic vibration of the belt drive). It is preferable to be able to rotate. Such a free stroke can be accomplished by one or both of two features, both shown in the drawing. First, the key 462 of the clamp sleeve 460 is formed to be narrower than the missing portion 472, so that a certain amount of rotational play can be provided to the pivot arm 420. In addition or alternatively, as shown in the figure, the clutch spring 480 may be formed with windings having a large diameter corresponding to two to three times, and a certain amount of rotational play may be incorporated into the assembly. The reason is that when the pivot arm 420 starts to rotate the clutch spring 480, the large-diameter winding in the clutch spring 480 first contracts and then contacts the lower surface, and then the clutch spring is clamped. This is because the main rotational torque is generated in the sleeve 460. As another modification (not shown), the number of turns of the coil of the clutch spring in the “stop sleeve (center portion of the arm)” 450 is reduced (or eliminated completely), and the cavity 421 is formed in the circumferential direction. By forming it into an arcuate shape, it is possible to provide rotational play even if the arm can rotate by a certain amount before the arm 420 of the tensioner presses the clutch spring to follow the rotation of the arm.

  In the embodiment of the present invention illustrated above, the reverse rotation stopper device is frictionally engaged with the pivot shaft 16 to prevent the reverse rotation stopper device from rotating. Even if the reverse rotation stopper device prevents rotation by frictionally engaging the base plate 30 or a fixed portion such as the engine body (when the base plate is not used), the tensioner can be configured. These and other embodiments are considered to be within the scope of the claims.

FIG. 1 is a front elevational view showing an internal combustion engine for a vehicle including a timing belt assembly including a tensioner. FIG. 2 is a cross-sectional view illustrating a tensioner according to an embodiment of the present invention. FIG. 3 is a perspective view showing a stop sleeve and a clamp holder in the tensioner of FIG. 4 is a perspective view showing a brake clamp in the tensioner of FIG. FIG. 5 is a cross-sectional view illustrating a tensioner according to another embodiment of the present invention. 6 is an exploded perspective view of the tensioner shown in FIG. FIG. 7 is an exploded perspective view showing a tensioner according to another embodiment of the present invention. FIG. 8 is a cross-sectional view showing an assembly relationship between the upper clamp sleeve and the lower bottom sleeve in FIG. 7, and the cross-sectional view is taken along a cut surface passing through the upper clamp sleeve. This is shown in the direction toward the pivot arm as indicated by line 8-8. FIG. 9 is a cross-sectional view illustrating a tensioner according to another embodiment of the present invention. FIG. 10 is a cross-sectional view illustrating a tensioner according to still another embodiment of the present invention. 11 is a cross-sectional view of the tensioner shown in FIG. 10 taken along line 11-11.

Claims (33)

  1. A belt tensioner for a vehicle engine,
    A pivot shaft,
    A pivot arm pivotally attached to the pivot shaft;
    A pulley rotatably supported by the pivot arm;
    A spring that biases the pivot arm in a direction in which the belt is stretched;
    A reverse rotation stopper device including a one-way clutch member and a friction brake member, wherein the friction brake member is fixed to a fixed portion by friction engagement, and the fixed portion is stationary with respect to the engine of the vehicle. The one-way clutch member is disposed between the pivot arm and the friction brake member, and the one-way clutch member rotates the pivot arm substantially freely in a direction in which the belt is stretched. And a reverse stopper device constructed and arranged to prevent the pivot arm from rotating relative to the friction brake member in a direction opposite to the direction in which the belt is stretched. ,
    A tensioner characterized by comprising:
  2.   The strength of the frictional engagement between the friction brake member and the fixed portion is opposite to the direction in which the belt is stretched when the pivot arm receives torque due to belt load under normal engine operating conditions. The pivot arm can only be rotated in the direction that is large enough to stop the pivot arm from rotating in the direction and that is opposite to the direction in which the belt is tensioned manually. The tensioner according to claim 1, wherein the tensioner is sufficiently small.
  3.   The friction brake member is configured to open at least partially when the pivot arm is rotated in the direction opposite to a direction in which the belt is tensioned manually. Item 5. The tensioner according to Item 2.
  4.   The tensioner according to claim 1, wherein the fixed portion is constituted by a portion of the pivot shaft in the vicinity where the reverse stopper device is disposed.
  5.   The tensioner according to claim 1, wherein a certain amount of play is provided between the pivot arm and the one-way clutch member.
  6.   6. The tensioner according to claim 5, wherein the play includes a predetermined rotation component that is substantially the same as the rotation magnitude of the movement of the arm caused by thermal expansion of the engine.
  7.   The play is substantially the same as the magnitude of rotation of the arm movement caused by thermal expansion of the engine and the magnitude of rotation of the arm movement caused by dynamic vibration of the pivot arm by the engine. The tensioner according to claim 5, comprising a predetermined rotational component.
  8. The friction brake member is composed of a friction clamp member,
    The one-way clutch member is composed of a pair of axially aligned rotating members disposed around the pivot shaft, and one of the rotating members is engaged with the pivot arm, The other of the rotating members includes a clamp holder that engages with the friction clamp member, and at least one of the rotating members has a cylindrical portion,
    The one-way clutch member further includes a clutch spring, and one end portion of the clutch spring overlaps the cylindrical portion of the at least one rotating member, and the other end portion of the clutch spring. Is attached to the other of the rotating members, whereby the clutch spring allows the rotating members to rotate in one direction relative to each other, and the rotating members in opposite directions to each other. Substantially prevent rotation,
    The tensioner according to claim 1.
  9.   The clamp holder is composed of an upper clamp sleeve member and a lower bottom sleeve member, and the friction clamp member is accommodated between the upper clamp sleeve member and the lower bottom sleeve member. The tensioner according to claim 8, wherein the tensioner is provided.
  10.   The tensioner according to claim 8, wherein the clutch spring is fixed to a rotating member engaged with the pivot arm by a protrusion of the clutch spring.
  11.   The tensioner according to claim 8, wherein the clutch spring is fixed to the clamp holder by a protrusion of the clutch spring.
  12.   The tensioner according to claim 8, wherein one of the rotating members of the one-way clutch member is formed integrally with the pivot arm.
  13.   The tensioner according to claim 8, wherein the pair of rotating members are directly coupled to each other in the axial direction.
  14.   The tensioner according to claim 13, wherein one of the rotating members of the one-way clutch member is formed integrally with the pivot arm.
  15. A belt tensioner for a vehicle engine,
    A pivot shaft,
    A pivot arm pivotally attached to the pivot shaft;
    A pulley rotatably supported by the pivot arm;
    A spring that biases the pivot arm in a direction in which the belt is stretched;
    A reverse rotation stopper device including an arm engagement portion, a friction brake member, and a one-way clutch member;
    The reverse stopper device allows a relative sliding movement between the one-way clutch member and the friction brake member, so that the pivot arm rotates substantially freely in a direction in which the belt is stretched. Allow to
    The reverse stopper device includes: an engagement by the arm engagement portion; a friction engagement between the friction brake member and a stationary portion stationary with respect to the engine; and the friction brake member and the arm engagement portion. A tensioner characterized in that the pivot arm is prevented from rotating in a direction opposite to a direction in which the belt is stretched by the coupling action of the one-way clutch member between the two.
  16.   The strength of the frictional engagement between the friction brake member and the fixed portion is opposite to the direction in which the belt is stretched when the pivot arm receives torque due to belt load under normal engine operating conditions. The pivot arm can only be rotated in the direction that is large enough to prevent rotation of the pivot arm in that direction and that is opposite to the direction in which the belt is tensioned manually. 16. The tensioner according to claim 15, wherein the tensioner is sufficiently small.
  17.   16. The tensioner according to claim 15, wherein the fixed portion is constituted by a portion of the pivot shaft in the vicinity where the reverse stopper device is disposed.
  18.   The tensioner according to claim 15, wherein a certain amount of play is provided between the pivot arm and the one-way clutch member.
  19. The friction brake member is composed of a friction clamp member,
    The reverse stopper device includes a pair of substantially cylindrical members arranged in the axial direction and arranged around the pivot shaft, and one of the substantially cylindrical members is engaged with the pivot arm. And the other of the substantially cylindrical members includes a clamp holder that supports the friction clamp member,
    The one-way clutch member includes a clutch spring, and the clutch spring overlaps the pair of substantially cylindrical members, and allows the substantially cylindrical members to rotate in one direction relative to each other. Substantially preventing the substantially cylindrical members from rotating in opposite directions;
    The tensioner according to claim 15, wherein:
  20.   The clamp holder is composed of an upper clamp sleeve member and a lower bottom sleeve member, and the friction clamp member is accommodated between the upper clamp sleeve member and the lower bottom sleeve member. The tensioner according to claim 19, wherein the tensioner is provided.
  21.   20. The tensioner according to claim 19, wherein the clutch spring is coupled to the substantially cylindrical member engaged with the pivot arm.
  22.   The tensioner according to claim 19, wherein the clutch spring is coupled to a substantially cylindrical member constituting the clamp holder.
  23.   The tensioner according to claim 19, wherein the pair of substantially cylindrical members are directly coupled to each other in the axial direction.
  24.   20. A tensioner according to claim 19, wherein a certain amount of play is provided between the pivot arm and the engagement portion of the generally cylindrical member engaged with the pivot arm.
  25. A belt tensioner for a vehicle,
    A pivot shaft configured to be secured to the engine;
    A pivot arm pivotally attached to the pivot shaft;
    A pulley rotatably supported by the pivot arm;
    A spring configured and arranged to bias the pivot arm in a direction in which the belt is tensioned;
    A reverse stopper device disposed between the pivot arm and a stationary part stationary with respect to the engine, wherein the reverse stopper device is substantially free in the direction in which the belt is stretched. The reverse stopper device configured and arranged to allow the arm to rotate and to prevent the pivot arm from rotating in a direction opposite to the direction in which the belt is stretched. ,
    The pivot arm and the reverse stopper device are configured to cooperate to provide a predetermined limited amount of rotational play between them,
    The reverse stopper device is a pair of stopper members disposed around the pivot shaft, one of the stopper members engaging with the pivot arm, and the other of the stopper members being coupled to the fixed portion. The stopper member, and a one-way clutch member, the clutch spring overlapping the pair of stopper members, allowing the stopper member to rotate in one direction relative to each other, A tensioner comprising: the one-way clutch member which substantially prevents the members from rotating in opposite directions.
  26.   26. The tensioner according to claim 25, wherein the other stopper member is directly coupled to the fixed portion via a friction brake member engaged with the fixed portion.
  27.   26. The tensioner according to claim 25, wherein the other stopper member is coupled to the fixed portion via a hydraulic device.
  28.   28. The tensioner according to claim 27, wherein the other stopper member is coupled to the fixed portion via a viscous substance.
  29. A belt tensioner for a vehicle,
    A pivot shaft configured to be secured to the engine;
    A pivot arm pivotally attached to the pivot shaft;
    A pulley rotatably supported by the pivot arm;
    A spring configured and arranged to bias the pivot arm in a direction in which the belt is tensioned;
    A reverse stopper device disposed between the pivot arm and a stationary part stationary with respect to the engine, wherein the reverse stopper device is substantially free in the direction in which the belt is tensioned. A reverse stopper device configured and arranged to allow the arm to rotate and to prevent the pivot arm from rotating in a direction opposite to the direction in which the belt is stretched. ,
    The reverse stopper device is a pair of stopper members disposed around the pivot shaft, one of the stopper members engaging with the pivot arm, and the other of the stopper members being fixed via a viscous substance. A stopper spring that is coupled to the portion, and a one-way clutch member, and a clutch spring that overlaps the pair of stopper members, the stopper members rotating relative to each other in one direction. A tensioner comprising the one-way clutch member that permits and substantially prevents the stopper members from rotating in opposite directions.
  30. A rotating device for selectively transmitting rotational output or rotational torque, a pair of rotating members that are directly coupled to each other in the axial direction and are rotatable relative to each other;
    A one-way clutch spring disposed so as to cover the pair of rotating members, the one-way clutch spring being connected to the pair of axial directions when one of the rotating members rotates in one direction; When the rotating member is interlocked in the rotation direction and one of the rotating members rotates in the opposite direction, the rotating member connected in the axial direction is allowed to relatively rotate. A directional clutch spring;
    A rotating device comprising:
  31.   One of the pair of rotating members has a ring-shaped edge disposed so as to cover a part of the clutch spring, and when the one of the rotating members rotates in the opposite direction, 31. The rotating device according to claim 30, wherein the winding of the clutch spring is restrained from being opened, and the winding is not opened by rotation in the opposite direction.
  32.   The clutch spring has at least one winding that has a larger diameter than the remaining windings of the clutch spring, and the clutch spring has the clutch spring paired with the pair of coils. 31. The rotating device according to claim 30, wherein a certain degree of free rotation stroke is provided to the one of the rotating members before interlocking the rotating member in the rotational direction.
  33.   One of the pair of rotating members has a ring-shaped edge disposed so as to cover a part of the clutch spring, and when the one of the rotating members rotates in the opposite direction, 33. The rotating device according to claim 32, wherein the opening of the winding of the clutch spring is constrained to prevent the winding from being opened by rotation in the opposite direction.
JP2003549763A 2001-12-05 2002-12-03 Tensioner Active JP4508641B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US33580101P true 2001-12-05 2001-12-05
PCT/CA2002/001854 WO2003048606A1 (en) 2001-12-05 2002-12-03 Timing belt tensioner with stops controlled by frictional brake

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JP2005511984A true JP2005511984A (en) 2005-04-28
JP4508641B2 JP4508641B2 (en) 2010-07-21

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JP (1) JP4508641B2 (en)
KR (1) KR100933816B1 (en)
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AU (1) AU2002347150A1 (en)
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EP1451486A1 (en) 2004-09-01
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US8267819B2 (en) 2012-09-18
AU2002347150A1 (en) 2003-06-17
US20060035740A1 (en) 2006-02-16
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US7507172B2 (en) 2009-03-24
KR100933816B1 (en) 2009-12-24
BR0214737A (en) 2004-09-14
EP1451486B1 (en) 2008-03-19
CN100439758C (en) 2008-12-03
DE60225716D1 (en) 2008-04-30
EP1788283B1 (en) 2012-01-18
WO2003048606A1 (en) 2003-06-12
DE60225716T2 (en) 2009-04-30
JP4508641B2 (en) 2010-07-21
KR20050044684A (en) 2005-05-12
BR0214737B1 (en) 2011-02-22
CA2469497A1 (en) 2003-06-12
US20090176609A1 (en) 2009-07-09

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